Gear grinding machine



n-nullllllUl Jan. 16, 1940. w. E. sYKEs GEAR GRINDING MACHINE Filed Dec. 4, 1937 9 Sheets-Sheet l .w11 #uw y@ -mv mb mi m m R .0 O w WM w Q@ m 1M A 3. #1 m TN, mi 4 -ll.. SQ.

Jan. 16, 1940. w. E. sYKEs GEAR GRlNDING MACHINE 9 Sheets-Sheet 2 Filed Dec. 4, 1937 ATTORNEY Y'Jan. 16, 1940. w; E. "SYKES 2,187,062

GEAR GRINDING MACHINE Filed Dec. 4, 1937 '9 Sheets-Sheet 3 ATTORN Jmlls, 1940.

W. E. SYKES GEAR GRINDING MACHINE Filed Dec. 4, 1937 9 Sheets-Sheet 4 WHW i y Q INVENTOR ATTORNEY Jan. 16, 1940.

w. E. sYKEs GEAR GRINDING MACHINE 9 Sheets-Sheet 5 Filed Dec. 4, 1937 Jan. 16, 1940. w E, SYKES 2,187,062

GEAR GRINDING MACHINE Filed Dec. 4. 1937 9 Sheets-Sheet 6 Snnentor M//la/n 569%.

fw @mm Jan. 16, 1940. w E, SYKES 2,187,062

GEAR GRINDING MACHINE :inventor mwa- Jan, 16, 1940. 'I w, E SYKES 2,187,062

GEAR GRINDING MACHINE Filed Dec. 4, 1937 9 Sheets-Sheet 8 C( meg Jan. 16, 1940. w, E, SYKES 2,187,062

l v GEAR GRI-NDING MACHINE Filed Dec.v4, 193'?I 9 Sheets-Sheet 9 Smaentor Patented Jan. 16, 1940 YUNITED STATES PATENT OFFICE GEAR GRINDING MACHINE William E. Sykes, Buiialo, N. Y. Application December 4, 1937, Serial No. 178,023

6 Claims.

This invention relates to a machine for finishing the teeth of gears, gear cutters, and the like, and it has particular reference to a machine operating on the generating principle and adapted to grind a wide variety of types and sizes of teeth y with reference to the accompanying drawings.

First, a means for mounting a tool such as a grinding Wheel for reciprocating movement in a lineal path. Second, means for mounting the work for oscillatory movement through an arc commensurate with the length of the surface to be finished, and effecting a timed relation between the motion of the tool and the motion of the work, to cause a tooth of the workand tool to contact through the desired curve to be generated. Third, means operable while the tool is removed from the work to advance or index the work, so that, upon a subsequent stroke. the tool will finish a new tooth. Such means, as hereinafter more fully described, includes an indexing mechanism which rotates the work one-half the distance between teeth while the tool recedes from the work, and the other half of the distance While the tool advances toward the work. thus reducing the inoperative or lost` motion phase of the tool movement to half the; time which otherwise would be required. Fourth, the provision of improved means for mounting the tool so that it may be correctly positioned to contact teeth of different pitches or shapes. Fifth, the provision of improved indexing means whereby an accurate adjustment and coordinated movement of the tool and work may be obtained.

While it is intended that the foregoing features of the invention may be used in conjunction with each other, it will also be understood that, as pointed out in several of the appended claims. they may on occasion be used in other relationships, and therefore it will be understood that the following description is intendedto exemplify, ratherthan limit, the invention as hereinafter claimed.

In the drawings:

Fig. 1 is a top view of the machine which is set up to grind a helical cutter;

Fig. 2 is an end view thereof with the grinding wheel positioned to grind a straight-tooth cutter;

Fig. 3 is a section on the line 3 2 of Fig. 2

showing the radial adjusting mechanism of the cutter head;

Fig. 4 is a front view of the machine as organized in Fig. 1;

Fig. 5 is an enlarged section on the line 5 5 6 of Fig. l showing the longitudinal swivel slide and associated adjustable mechanism which supports the lateral grinding Wheel carriage;

Fig. 6 is an enlarged section through the headstock taken on the line 6 6 of Fig. l;

Figs. 7 and 8 are enlarged front views of the index head in positions at the end of the clockwise and counter-clockwise movements, respectively. Portions of these views are broken away or sectioned to show underlying mechanism;

Flg. 9 is a section on the line 9 9 of Fig. 6, constituting a rear view of the index head in the position of Fig. 8;

Fig. 10 is an enlarged section on the line M itl of rig. s; 20

Fig. 11 is an enlarged section on the line i il of Fig. 8;

Fig. 12 is a section on the line I2 l2 of Fig. 10, showing the reversing transmission and associated mechanism in the phase of indexing move- 25 ment shown in Fig. 7;

Fig. 13 is a section on the line I3 |3 of Fig.

10, showing the locked position of the transmission, which position is maintained after the completion of the indexing movement (as in Fig. 8); 30

Fig. 14 is a diagrammatic view of the gear train of the indexing mechanism; A

Fig. 15 is a perspective view of the pawl carrier and a clutch gear of the reversing mechanism;

Fig. 16 is an enlarged front view of the indexing tumbler;

Fig. 17 is a front view of the band pulley;

Fig. 18 is a section on the line |8 I8 of Fig.

1, showing the main carriage crank mechanism;

and i l Fig. 19 is asection on the line I 9 i9 of Fig. 7. The machine includes a base 25 having ways 26, 21, 28 for receiving-a main grinding wheel carriage 30, which is formed with cooperating slides 3i, 32, 33. The carriage 30 carries a multiplicity of adjustable mechanisms for accurate- 4ly positioning av motor driven grinding wheel G with reference to the work piece C, which may be a gear cutter or other toothed device. (Figs. 1 to 5.)

The right hand extremity of the base 25 (Figs. 1 and 18) is formed with a bracket portion35 to which is secured a motor 38 and a connected reducing gear unit 31. which contains a suitable 56' in a bracket 41, which in turn-is secured to the carriage 30. The throw of the crankshaft and the associated reciprocatory movement of the carriage. may thus be varied to suit the nature of the grinding operation.

The base is provided with a laterally\ projecting portion 50 which serves as a mounting base for a rigidly secured headstock unit 48. The unit includes a rotatable work spindle 5| and a pulley 52, which is connected to the shaft through an. automatic indexing mechanism 59, as will presently be more completely described.

The pulley 52 and accompanying work spindle 5| are oscillated in timed relation to the reciprocation of the carriage 30 through a direct driv- -ing connection (Figs. l and 4) A channel member 54 is secured to the front face of the carriage 30 and it is formed with spaced projecting arms 55, 88, on which vertically slotted pedestals 51, 58 are mounted in aligned relation. Bands 8|, 52 'are secured to the pedestals 51, 88. respectively, by attached screws 8 8 which are secured to the slotted portions of the pedestals by nuts 84. The free ends of the bands are wrapped l about the pulley 52 and secured by screws 85 (Fig.A 6). 4When properly positioned and tensioned, the

bands provide an extremely effective connection which transforms the lineal reciprocatory movement of the carriage intoalternate clockwise and counter-clockwise rotation of the pulley 52. The

work piece or'cutter C is secured to the end of the work spindle 8|, and the grinding wheel G is correctly positioned so\that it contacts one side of a rtooth of the cutter during the eycle of movement of the carriage 90.

The various adjustable mechanisms carried by the carriage are utilized to bring the wheel G y into proper grinding relation with the teeth of the work piece, which may be of helical or straight formation. The stroke of the carriage 90 may be varied in accordance with the diameter and tooth depth of the work piece by stroke adjustment o! the crankshaft 89 through its movable slide 42,'

so that the wheel G travels a suiilcient distance to grind the entire face and iiank of a tooth of the rotating work piece.

The longitudinal positioning of the supporting structure of the grinding wheel on the carriage I0 is controlled by a slide l.81 (Figs. 3 and 5) which i's provided'with gib portions 88, 69, whichengage longitudinally extending ways 1| formed on theuppersurface of the carriage 80. The slide 81 is formed with a nut 'portion 12 (Fig.` 3) for receiving an adjusting screw 10 which extends through a bearing 18 on the carriage and is operated by an adjusting crank 14. The'entire supporting structure of the grinding wheel may thus be' shifted on the main carriage 30 to bring the .grinding wheel into a centralized positionv relativen its stroke and/to the unaemmg workpiece C.

'I'he supporting structure may be moved to any desiredangular position about a vertical. axis in order that the face of th'wheel G may be given the proper angle fongrinding helicalor straight teeth. The longitudinal slide 61 is provided with acircularh'ead 15 formed with`a concentric T-A `animes slot 18 for receiving T-bolts 11. A complementary swivel head 18 is rotatably mounted on they head 15 and it is provided with suitable holes 19 for receiving'the ends of the bolts 11.' Nuts 8| on the bolts 11 permit the heads 15 and 18 to be clamped together at any desired rotative position.

Horizontal ways 83 form part of the swivel head structure, and they receive the gib portions 85a of a cross carriage 85. A screw 85 is iixed in bosses 81, 88 of the carriage 85, and it receives a nut 89 which is rotatably carried in a bearing 9|, forming part of the underlying swivel head 18. 'I 'he swivel head 18 and slide head 15 are formed with aligned axial bearings 92, 92a for a countershaft 99 on which are secured bevel gears 94, 95. lThe gear 94 meshes with a bevel gear 98 forming part of the nut 89, while the gear 95 engages a bevel gear'91, which'is secured to a lateral adjusting shaft |00, carried in bearings 98, A99 in the slide-81 (Fig. 5). l

The projecting extremity of the shaft |00.is

formed with a squared portion |0| for receiving a with reference to the teeth of the work piece is obtained through adjustment of a horizontal swivel head ||0 on a circular head portion iii formed on the. extremity of the cross carriage 85. These elements are clamped together by T- bolts ||2 positioned in a circular T-slot ||9a in the head portion I and extending through suitable holes in the horizontal swivel head ||0. A segment gear ||3 is secured to the head H0, and .it is engaged by an adjusting worm H4 whose shaft ||8 is journalled ina bearing member it@ which is fastened to the head portion l. -The clamping bolts I2 may be -loosened to permit operation of the shaft ||5 and the adjustment of the head ||0 about a horizontal axis.

The head is provided with ways |09 which `receive the gib portion ||1 of. a wheel saddle M8 which is formed with spaced bearing portions H9 disposed on a transverse axis relative to the ways |09. A wheel shaft |20 is mounted in the bearing portions |9 and it is formed with tapered spindle portions |2|, |2|a. The grinding wheel G. as "shown infthe drawings, is secured to the right hand spindle portion |2| by a lock nut |22.

An adjusting screw |23 is mounted in a bear- 'in'g |24 in the horizontal head ||0, and it engages a nut portion |25 formed on the wheel saddle I8. This screw permits the wheel saddle ||8 and accompanying wheel to be raised or lowered to proper depth 1-engagement with the teeth of the work piece. The wheel shaft |20 carries a is, longitudinally, transversely, and vertically. In l0 addition, the two swivelhead assemblies permit the wheel faceto be disposed in any desired vertical and/or horizontal angular position. The former, or special adjustments permit the grinding wheel to be brought into registry with work pieces of'any diameter, while the angular adjustments permit the wheel to be set to the pressure and helix angles dictated by the tooth formation of the workpiece.

'I'he machine is especially adapted to grind the teeth of large cutters of the type shown, 1n which the rotating grinding wheel G may be rigidly xed in an accuratelyradjusted position with reference to its main carriage 30. The duty of the grinding wheel for this type of work consists in properly molding the profile of the cutter teeth for a short space adjacent the cutting face F of the cutter. In other clases of grinding work where the entire width of gear teeth, for example, must be ground, the cross carriage may be moved through the ratchet feed to cause the wheelv G to move in small increments across the face of the work.

. Indexing mechanism The pulley or drum 52 is slotted, as indicated by the numeral |30, to permit its removal from the headstock assembly without disturbing the spindle 5i (Fig. 17). 'Ihe pulley is secured by screws |3| to a anged member |32, which in turn is keyed to one end of a hollow drum shaft |33 which encompasses the spindle 5| (Fig. 6). A'pedestal |34 is secured to the base portion 50, and it is provided with spaced bearing portions |36, |31, the latter of which contains ball bearings |38 for rotatably supporting the drum shaft |33. The right hand portion of the drum shaft is formed with a ilange |39 to which a cylindrical index unit' housing |40 is rigidly secured by screws |44. The outer extremity of the shaft |33 is shouldered to receive ball bearings |43 which are secured by an aixed retainer |44.

'I'he work spindle 5| is formed with an enlarged arbor portion |45, to which the work piece C is clamped by a suitable locking device |46. 'I'he spindle is rotatably mounted in a ball bearing |41 located in the bearing portion |36 of the pedestal |34, and thence it loosely projects through the drum 52 and the hollow drum shaft |33. An adapter |40 is keyed to the extremity of the spindle, and it is retained by a nut |49 which engages the threaded end of the spindle.

The adapter is formed with a cylindrical projection |5| which receives the ball bearings |43 of the drum shaft 33. A gear |53 is secured to a radial flange |5|a .on' the rear of the projection |5|, while the front end of the adapter is shouldered to receive an index plate or anchor wheel |50 which is secured by screws |55.

The work spindle 5| and the described parts which are rigidly secured to it are thus mounted for rotation independently o1' the drum shaft |33 and accompanying index unit housing |40. 'Ihe indexing mechanism, which first couples these independent units and then causes their controlled relative movement during each oscillatory cycle of the drum, will now be described.

A large worm wheel |60,l whose body |59 serves as a mounting plate for the variousv indexing instrumentalities, is formed with a hub |6| which is rotatably mounted on the projection |5| of the adapter |48. A worm |62 is secured'to a shaft The wheel body |59 carries on its rear face` Springs |69 mounted on pins |1| retain the plate infrictional contact with the face of the large adapter gear |53, so that when the Work spindle and drum shaft assemblies are momentarily disconnected, as occurs during each oscillation, sufcient frictional contact is provided to prevent lag or over-run, which may be caused by inertia effects.

A guide member |13 is secured to the front face of the wheel'body I 59, and it is formed with a gib portion |14 for receiving a plunger slide |15. A tooth |10 projecting from the slide |15 is adapted to enter one of the notches |50a of the anchor wheel |50. A spring |16, extended between pins |11, |18, on the slide |15 and guide member U13, respectively, retains the tooth 10 in engagement With one of the notches |50a. Removal of the tooth |10 is controlled by a lever |19 (Fig. 8) having one end engageablewith a roller 682 carried on the slide pin |11. A connecting rod is connected to the lever |19 by a stud |84 and it extends to an indexing transmission for timed operation with the indexing movement when it is thrust upward to move the lever |19 and thus disengage the slide tooth |10 from the anchor wheel |50.

In the. present machine arrangement, the indexing movement is instituted near the end of the clockwise movement and continues during an equal arcuate movement on the return or counterclockwise movement of the index housing. As

shown in Fig. '1, at the end of the vfirst half of the movement the anchor wheel has been caused to rotate in advance ofthe index housing for a distance equal to one-half of the notch spacing on the anchor wheel. During the remaining or return half of the movement, a similar relative movement occurs, so that the total movement of the anchor wheel is precisely one notch space. To simplify the description, the anchor wheel and cutter C are assumed to have an equal number of notches and teeth respectively; thus it will be apparent that during each indexing movement a new cutter tooth is presented to the grinding wheel.

The actuating means for the indexing transmission |85 consists of a iixed abutment in the form of a bar |81 which is carried in bearings |88 in the pedestal portion |31. In its operative position (dotted lines, Fig. 6) the forward end of the bar is positioned within the housing |40, a suitable arcuate clearance slot |89 being formed in the housing for this purpose (Fig. 9). When automatic indexing is not desired, the bar is moved to an inoperative position (full lines, Fig. 6) by a lever |9| which is carried by a manually operable shaft |92. 'Ihe end of the lever is formed with a nger |93 which engages in a shouldered portion |94 of the bar. The end of the bar |91 is supplied with a cam roller |909 The worm wheel body |59 is suitably bored to form a transmission housing |96, which is completed by the application of cap plates |91, |98 (Fig. 11). A cam shaft |99 carried in bearings 20|, 202 in the cap plates, is formed with a projection 203 to which is secured a tumbler lever or cam 200. The lever is formed with arms or lobes 204, 205, 206, and it is disposed to engage theI roller of the bar |81 during oscillation of the housing |40. The housing and accompanying worm wheel |60 are so positioned that when they approach the termination of their counter-clockstroke (Figs. s and 9), the arm zu strikes the roller |90 and is rotated until it the same. -During this rotation the opposing or central arm 205 is brought into a position (Fig. 7) where, on the subsequent return stroke, it strikes the roller l|90 to restore the arm 209 to its :llrst position. The arm 209 is not used in the present of the connecting rod |90 is supported during the non-indexing movement of the housing |40. As the shaft |99 1s rotated during the rst half of the indexing movement, the rod end is caused to ride on the periphery of the flange 209, and being thus moved outward, it actuates the lever |19 and lcauses the tooth |10 to be moved out of engagement with the anchor wheel |50. Atl the terminationof the return half of the indexing movement, the rod end is re-positioned in the cam fnotch, as before, 'The rod end |8 0a is guided in ansiosa a bearing 2|| in the cap plate |91, with provision being made for a slight lateral movement therein to prevent binding and to provide a short dwell (Figs. 12 and 13)."

Gears 2|0 and 220 are rotatably carried on the Ashaft |99 and they are disposed on opposite sides ofthe control disc 200. The disc is formed to receive spring pressed pawls 2|3, 2|4, which are adapted to engage in detents 2|0a,` 220e. in the adjacent faces of the gears 2|0 and 220, respectively (Fig. 15). r

The gear 2| 0 meshes with a gear 2|5, whose integral companion gear- 2|5a meshes with a gear 2|1 (Figs. 10, 11, and 14). The gear 220 directly meshes with the companion gear 2|1a of the gear 2|1. The cluster gear 2|5, 2|5a isrotatably car- 'ried on a stud 2|9 secured to the body |59, while the cluster gear 2|1, 2|1a is keyed to a shaft 22| which is supported in bearings 222, 223 in the cap plates |91 and |99, respectively.

The shaft 22| is connected to operate' a final shaft 225 through a group of change gears consisting of a gear 229 secured to the shaft 22|, an

intermediate .idler gear 221, and a gear 229 se` cured to the shaft 225. The idler gear 221 is mounted on a stud 229 which is positioned in the slot 23| of an adjustable arm 232.

The nal shaft 225 projects lthrough a bushing 233 in' the body |59, where a pinion 230 is keyed to it. This pinion meshes with the large gear |53 which forms part of the work spindle assembly (Flgs. 9, 11, 14), thus` providing a'driving connection through which differential movement between casing and spindle may be obtained.

The operation of the indexing mechanism is as follows: The drum and work spindle assemblies are united by the connection between the tooth |10 and anchor wheel |50, so that they rotate as one during a' major portion of the oscillation of the drum.l When they approach the-end of their 'clockwise movement, however, the tumbler lever Strikes the stationary roller |90 of the bar |91 and is rotated. During the first phase' of rotation, the connecting rod |90 is forced out Vof its cam notch 201, thus disengaging the tooth |10 from the anchor wheel |50. `Furtherv pinion 290,'to the large gear |53. 'The gears are properly chosen so that the large gear |59 and accompanying anchor wheel |50 are rotated in advance of the housing |40 an angular distance equal to one-half ofthe circular pitch of thek notches |a of the anchor wheel (Figs. 7 and 12) Shortly after the tumbler lever is rotated to its full extent, the housing |40`arrives at the end of its clockwise stroke and immediately starts its counter-clockwise stroke. 'Ihe tumbler lever, il)

which is now positioned with its central arm 205 disposed nearly radially (Fig. 7), again engages the cam roller of the fixed bar |91. The lever is thus turned in passing, and it is restored to the position of Fig. 9. Its direction of rotation, however, is opposite to that in the previously deineffective during this movement, and simply ride l past their detents.

The gear 220, being thus driven, transmits movement directly to the cluster gear 2|1 (Figs. l2 and 13) which, through the change gear'train, causes rotation of the final shaft 225 and drive pinion 230 in the same direction as they were rotated during the described first movement. The large gear |53 of the work spindle is thus rotated clockwise relative to the housing |50A for an angular distance equal to the remaining half of the circular pitch of the notches |50a. At this time, the connecting rod end re-centers the cam notch 201, and the tooth |10 is'accordingly caused to drop into the newly presented notch in the anchor wheel |50.

It will now be obvious that a complete indexing movement occurs each time the main carriage 30 completes its cycle. Thus, as 'the grinding wheel G moves to the right out of grinding contact with a tooth of the cutter C,the indexing mechanism is set in motion, and, as the carriage 30 approaches the right hand limit 'of travel, one half of the indexing cycle is completed. As the ,carriage returns, the remaining half of the indexing is accomplished, and the work spindle and drum assemblies are locked for common movement.' By this action, the face of aj new tooth is presented which, immediately after the locking action, is engaged by the wheel G. The face of this tooth is progressively ground as the carriage moves to its left hand llimit of travel, where the wheel and tooth are temporarily disengagedv and immediately reengaged during the return movement of the carriage, when the same lface of the tooth is ground for a second time in a nish operation.

It will be understood thatlin this series ofl progressive operations, only the iight hand or obtuse sides of the helical teeth are ground. To grind the opposite or acute sides of the teeth, it has been found preferable to'remove the work piece from the work spindle and to turn it about and secure it to the spindle with the" cutting face F facing the indexing unit.'\The grinding wheel G is now mounted on the grinding spindle I2Ia, and then it is positioned through the adjusting mechanisms into correct contact with the teeth of the workV piece or cutter C .for operation as before.

- Adjustments In the grinding of right hand cutters orgears, it is preferred that the indexing movement occur at the end of the counter-clockwise movement of the housing |40. For this purpose, the tumbler lever 200 is turned approximately 160 degrees, so that the arm 206, rather than the arm 205, is presented to the abutment roller |90.v The cam shaft is provided with a hexagonal collar 240 (Figs. 10 and 16) for this adjustment, and in addition the lever 200 is formed with detents 24| for receiving a spring pressed plunger 242 which is carried in the adjoining portion of the cap plate |98. The detents 24| are located to receive the plunger, and thus to permit the operator to nd the correct positions of the cam lever during adjustment. A second cam notch 20'la is formed in the control disc 208 to provide actuating means for the connecting rod |80 in the now changed position of the control disc.

'Ihe more exacting adjustment of bringing-the cutting Wheel into the desired cutting contact with the work is controlled independently of the described wheel positioning mechanisms by means of the adjusting Worm |62 (Figs. 8 and 19). 'Ihe Worm shaft |63 projects through the bearing |65, where-it receives a small worm wheel 244 which meshes with a worm 245 mounted in suitable bearings. An adapter plate 246 is removably secured to the bearing |65, and it carries a stud 247 on which one end of a bearing bracket 248 is mounted for swinging movement. The remaining end of the bracket is slotted to receive a'clamping screw 249. The bearing bracket is formed with bearings 25| which receive the shaft 250 of the worm 2145.

A knurled handle 252, secured to the shaft 250, is adapted to be manually rotated to operate the reduction gear train for slight rotation of 'the worm |62 and the corresponding advance of the large worm wheel |50 relative to its housing |40. This, of course, directly causes the tooth of the work piece to be brought into closer or more remotecontact with the grinding wheel G. 'Ihe movement through the Worm 245 and worm wheel 244 provides a very fine adjustment of the wheel to the work, and it is not desirable when a rougher and more rapid adjustment is indicated. In this case, the bearing bracket 248 is swivelled about the stud 241 to disengage the worm 245 from the wheel 244, and application of a suitable crank in the holes 254 of the Wheel then permits direct actuation of the shaft |63.

It will be apparent that the construction of the adjusting mechanism for the worm |62 provided -in the adapter plate 246 also permits of rapid hand indexing without interfering with the parts contained Within the lhousing |40, beyond, of course, the simple withdrawal -of the bar |81 to render the automatic indexing mechanism inoperative.

The diameter of the drum 52 should be equal to the diameter of the base circle of the work piece C, to form perfect involute teeth. Different work pieces will therefore require different drums, which may be readily applied or removed by virtue of the provision of the slot |30. When a new drum is applied, the bands 6|, 62 are repositioned and tensioned in the slotted pedestals l,

58 to be parallel with the ways of the carriage 30,v thereby maintaining a constant angle of contact with the drum as the carriage reciprocates.

In practical use of the present invention, it has been found that not only may gears and cutters of ordinary size be nished with a high degree of accuracy, but that cutters for extremely large gears (and therefore the gears themselves) may be nished Within tolerances which have heretofore been attained only in smaller gears.

It will also be understood that while a single embodiment of the invention has been described in detail, those skilled in the art may resort to various modications Without departing from the spirit thereof as set forth in the following claims.

I claim:

1. In a machine of the character described, a relatively rotatable work holding spindle and an index casing mounted in coaxial relation, an indexing mechanism comprising means for imparting oscillatory movement to the casing, means connecting the casing and spindle, for unitary oscillation, control means for said connecting means for disconnecting the casing and spindle, actuating means for the control means carried by the casing and being operable during minor sectors of movement in opposite directions at one end of the oscillatory stroke of the casing, and a driving transmission for said spindle operated by and during operation of said control means.

2. In a machine of the character described, a relatively rotatable Work holding spindle and an index casing mounted in coaxial relation, means for oscillating the casing, indexing means con necting the casing and spindle for a major portion of the oscillatory stroke of the casing, and means associated with the indexing means for causing a movement of the spindle relative to the casing, said last named means including a driving connection between the casing and spindle, actuating means for the connection, and xed means engageable to move the actuating means during minor sectors of movement in opposite directions at one end of the oscillatory stroke of the casing.

3.. In a machine of the character described, a relatively rotatable work holding spindle and an index casing mounted in coaxial relation, means for imparting oscillatory movement to the casing, indexing means including a transmission connecting the casing and spindle for differential movement, cam means connected to operate the transmission, xed means engageable with the cam means during minor sectors of movement in opposite directions at one end of the oscillatory stroke of the casing, and means controlled by saidtransmission for connecting the casing and spindle for unitary movement during the remainder of the oscillatorycycle of movement of the casing.

4. In a machine of the character described, a relatively rotatable work holding spindle and an index casing mounted in coaxial relation, means for imparting oscillatory movement to the casing, a driving connection between the spindle and casing, a pair of operating mechanisms for the driving connection, said mechanisms being operable in opposite directions to drive the spindle in one direction relative tothe casingv through said driving connection, a rotatable clutch mechanism on the casing provided with means for engaging one mechanism when rotated in one direction and the remaining mechanism when operated in the opposite direction, a cam connected to the clutch mechanism, fixed means engageable with the cam during minor sectors of movement in opposite directions at one end of the oscillatory stroke of the casing, and means for imparting oscillatory movement to the easing, w

indexing means including a transmission connecting the casing and spindle for diilerential movement, a cam connected to operate the trans-- mission and formed with opposed lobes, fixed -means alternately engageable withthe lobes of the cam during minor sectors of movement in opposite directions at one end of the oscillatory stroke of the casing, and means controlled by said dle and index casing.

index casingmounted in coaxial relation, means a worm wheel mounted axially in the casing, a

- worm carried by the casing and meshing with the worm wheel, a second worm wheel secured to said worm, an adjustable worm meshing with the second worm wheel, bearing means on the cas- -ing supporting the adjusting worm, said means being movable to disengage the adjusting worm to permit direct operation of-said flrst worm,

` for imparting oscillatory movement to the casing.

and an indexing mechanism connecting the spin- WULIAME. SYKEB. 

